Methods for the preparation of dhea derivatives

ABSTRACT

An apparatus for shaping a flexible web ( 2 ) includes, between an entry roller ( 5 ) and a forming roller ( 3 ), a regulating module ( 7 ) provided with a starting roller ( 13 ) designed to control the movement and the speed of the web upstream of the shaping roller ( 3 ) and at least one mobile guide element ( 9 ) designed to exert, at least on one buffer loop ( 8 ) of the web ( 2 ) formed between the rollers ( 5, 3 ), a positive guiding thereof, in accordance with a law of displacement which is a function of the length of the buffer loop ( 8 ) in operation.

The present invention relates to an apparatus intended to ensure shaping of a web made of a flexible material, such as in particular a web of cardboard, from shaping rolls provided with plates of which the format is variable and interchangeable.

It is known for example that, in the domain of rotary cutting-out, the cut-out rolls as well as their associated control pinions must be changed when it is desired to pass from one format to another. Now, most of the time, these rolls are machined in the mass, so that this operation of replacement is translated by a particularly high cost.

In order to reduce this cost, it has been proposed to produce cut-out rolls which are constituted by a support roll, on the surface of which is fixed an interchangeable plate which is provided with cut-out threads. Such a device allows a rapid exchange and is translated by a reduced cost when one passes from one plate to another. Such an exchange is thus effected without problem, as long as the cut-out format remains unchanged from one plate to the other.

However, when such is not the case, one is then obliged to change the support roll as well as its accessory drive means.

The present invention has for its object to overcome such a drawback by proposing a shaping apparatus provided with a regulating module making it possible to use plate support rolls of a constant diameter on which the user will fix, as a function of his needs, work plates of diverse format, without it being necessary for all that, when he will pass from one plate format to another plate format, to exchange the support roll and its drive means.

In other words, the present invention makes it possible for the user to exchange only the shaping plates in order to pass from a determined work format to another format, within the limit, of course, of the peripheral length of the roll.

The present invention thus has for an object an apparatus for shaping a web made of a flexible material, comprising at least one feed roll adapted to deliver the web continuously in accordance with a law of given displacement and speed, a shaping roll associated with a counterpart roll adapted to shape the web over at least a part of its peripheral length, this shaping roll being constituted by a support roll on which at least one interchangeable shaping element is added, fixed on its outer surface, and which is animated by a movement of rotation in accordance with a law of given displacement and speed, characterized in that it comprises, between the feed roll and the shaping roll, a regulating module provided with take-off means adapted to control the displacement and the speed of the web upstream of the shaping roll and at least one mobile guide element adapted to exert on at least one buffer loop of the web formed between said rolls, a positive guiding of which the displacement is controlled in accordance with a determined law.

According to the invention, the law of displacement of the mobile element for guiding the web will preferably be a function of the law of displacement of the feed roll and of the law of displacement of the take-off means, itself a function of the law of displacement of the shaping roll.

The take-off means will preferably be constituted by at least one roll.

The take-off means may also be constituted by the mobile guide element, the latter being formed by a rotary roll around which the web winds; at least one rotary roll animated by a peripheral speed greater than that of the web being disposed between the shaping roll and the guide roll.

The guide element may be constituted by a rotary roll, or by a piece fixed in rotation, about which the web will wind. Particularly when the guide element is constituted by an element fixed in rotation, it may be provided with means for blowing a gas adapted to create between itself and the web a cushion of gas.

The movement of displacement of the guide element may in particular be linear or circular.

When the displacement is linear, it may be obtained by a linear motor comprising primary and secondary poles mobile with respect to each other and means for controlling their relative movements, the guide element being fast with one of these poles. This linear displacement of the guide element may also be obtained by a system constituted by a connecting rod articulated at one of its ends on the latter and at its other end on a crank whose angular position will determine the linear function of the guide element.

When the displacement is circular, the guide element will be constituted by a guide roll arranged so that it is adapted, in the course of its displacement, to remain tangential to another roll, the web being admitted between these rolls and winding around the latter in order then to go in the direction of the shaping roll.

This other roll may be constituted by a regulating roll or equally well by the take-off roll.

In order in particular to minimize the forces of friction exerted on the web, the guide roll and the regulating roll may be servo-controlled by each other in rotation, so that their peripheral speeds are identical.

According to the invention, the circular displacement of the guide and regulating rolls may ensure controlling of position and of speed of the web upstream of the shaping roll. The apparatus may, furthermore, comprise, between the feed roll and the take-off roll, a system for controlling the tension of the web by which the feed roll may be servo-controlled, so as to ensure maintenance of the tension thereof at a constant value.

Finally, the apparatus may comprise means adapted to read a cyclic mark disposed on the web, to compare the position thereof with a position reference of the shaping roll and, as a function of this comparison, to modify the positioning of the web with respect to the shaping roll.

A form of embodiment of the present invention will be described hereinafter by way of non-limiting example, with reference to the accompanying drawing, in which:

FIG. 1 is a schematic view of a cut-out apparatus disposed in a printing machine.

FIG. 1 a is a schematic view of a variant embodiment of the printing machine shown in FIG. 1.

FIG. 1 b is a schematic view of a variant embodiment of a guide element used in the apparatus according to the invention.

FIGS. 2 a and 2 b are partial schematic views showing cut-out rolls in two respective positions, namely a first position corresponding to the end of the cut-out phase and a second position corresponding to the beginning of the cut-out phase.

FIG. 3 is a schematic view of a variant embodiment of a shaping apparatus according to the invention.

FIG. 4 a is a diagram respectively representing the speed of feed of the web, the peripheral speed of the cut-out rolls, the speed of feed of this web directly upstream of the cut-out rolls, the speed of the roll of the regulating loop of the web, and this, on the one hand, during the cut-out phase and, on the other hand, during the end-of-cycle phase.

FIG. 4 b is a diagram respectively representing the positioning of the feed of the web, of the periphery of the cut-out rolls, of the feed of this web directly upstream of the cut-out rolls and of the roll of the regulating loop of the web, and this, on the one hand, during the cut-out phase and, on the other hand, during the end-of-cycle phase.

FIG. 5 is a diagram of the same type as that of FIG. 4 a in a form of embodiment of the present invention in which the speed of feed of the web to be cut out varies in the course of a cut-out cycle.

FIG. 6 is an example of a variant application of the shaping apparatus according to the invention.

FIG. 7 is a schematic view of a variant making it possible to constitute a regulating loop employed in an apparatus according to the invention.

FIGS. 8 and 10 are schematic views of two other variant embodiments of the apparatus shown in FIG. 7.

FIG. 9 is a schematic view of a variant embodiment of a mobile guide element according to the invention.

FIG. 1 shows a shaping apparatus 1 of a printing machine, intended to effect a cut-out operation. This shaping apparatus is constituted by a cut-out roll 3 and its counterpart roll 3′, which are animated by a movement of rotation at a peripheral speed V_(c), between which a web of cardboard 2 to be cut out is admitted at a speed V_(n), this web 2 being delivered by a feed roll 5 and its counterpart roll 5′, at a peripheral speed V_(e).

The cut-out roll 3 and its counterpart roll 3′ are constituted by a support roll 3 a on which a shaping plate, for example a cut-out plate 3 b, is fixed. As a function of the work to be carried out, this cut-out plate 3 b may be more or less long, so that it will occupy a more or less great part (p) of the total periphery P of the cut-out roll 3.

Under these conditions, it will be understood that, unless a considerable proportion of the web (equal to P−p/P) is wasted, it is necessary to provide that, as soon as the cut-out phase is ended, corresponding to the position of FIG. 2 a, the web 2 be stopped while the cut-out roll 3 and its counterpart roll 3′ determine their cycle of rotation (End-of-cycle phase). Moreover, for the subsequent cut-out operation to be able to run normally, it is also necessary that, at the moment of the beginning of the following cut-out, and during the whole cut-out operation, the speed V_(n) of the web 2 occurring between the cut-out rolls be the same as the peripheral speed of these latter, viz. V_(c), this making it necessary to cause the web 2 to go back during the end of the cycle for shaping the cut-out rolls 3, in order then to return it forwards to communicate thereto the speed V_(n)=V_(c) all along the cut-out.

It is for that purpose that a regulating module 7 has been disposed between the feed rolls 5 and the cut-out rolls 3. This regulating module makes it possible to produce a loop 8 forming “buffer” and allows that part of the web 2 located just upstream of the cut-out rolls 3 to stop, and even to move back, although the feed rolls 5, 5′ continue to feed the web 2 at a speed V_(e).

The regulating module 7 is constituted by a guide element, here constituted by a guide roll 9, around which the web 2 winds, and by a take-off roll 13 provided with a counterpart roll 13′ between which the web 2 is engaged. Unlike the “buffer” bands of the prior state of the art, this band is thus guided positively, i.e. it is maintained by an element whose position is determined mechanically or electronically, so that the displacement of the guide roll 9 is servo-controlled by the movement of displacement of the loop 8 and more precisely by the length thereof, and not by an element whose position is determined by the band itself, as is the case, for example, when a pulley or a roll is in gravitational abutment on the base of the band. It has been ascertained that such an arrangement made it possible to attain much higher operational speeds. The guide roll 9 is mounted to rotate about its shaft 14 and the latter is supported by a carriage 15 adapted to effect a linear movement in a vertical direction perpendicular to the horizontal direction of displacement of the web 2. The displacement of the carriage 15 may in particular be ensured by a linear motor, by a connecting rod/crank system, or by any other appropriate mechanism. In the present form of embodiment, the take-off roll 13 and the feed roll 5 are disposed in such a manner with respect to the guide roll 9 that the two web sections 2 a located upstream and downstream of the latter are parallel. FIG. 9 thus shows an example of a means for linear displacement of a guide element 9′ with the aid of a system constituted by a connecting rod 10 articulated at one of its ends on this guide element 9′ and at its end on a crank 12 whose angular position determines that of the guide element 9′.

Of course, the guide roll 9 may be fixed in rotation or, as shown in FIG. 1 b, it may be other than a rotating roll and may be formed by a fixed guide element 9′, for example a semi-cylindrical one.

FIGS. 4 a and 4 b respectively show, during a cycle of rotation of the cut-out rolls 3, on the one hand, the diagram of the speeds, and, on the other hand, the diagram of the relative positions of the feed rolls 5 (viz. V_(e), X_(e)), of the cut-out rolls 3 (viz. V_(c), X_(c)) of the web directly upstream of the cut-out rolls 3 (viz. V_(n), X_(n)) and of the guide roll 9 (viz. V_(t), X_(t)) and this for a plate element 3 a whose length p represents ⅗ of the periphery P of the cut-out rolls 3 (viz. p/P=0.6).

It is thus ascertained that the position X_(t) and the speed of vertical displacement V_(t) of the guide roll 9 are respectively a function of the positions X_(e), X_(n), on the one hand, and of the speeds V_(e), V_(n) on the other hand, viz. X _(t) =f(X _(e) , X _(n)) V _(t) =f(V _(e) , V _(n))

In the case of the form of embodiment shown in FIG. 1, and since the sections 2 a of the web 2 located upstream and downstream of the guide roll 9 are parallel, the following will be had: X _(t)=(X _(e) −X _(t))/2 V _(t)=(V_(e) −V _(n))/2 and the carriage 15 will be animated by a movement which will be a function of this law of displacement X_(t) and of speed V_(t).

The present invention makes it possible to control the loop 8 which, due to the aerodynamic phenomena and the inertias, is capable of disturbing, particularly at high speed, the advance of the web 2 and its positioning, both in the longitudinal and transverse direction, under the shaping plate.

Of course, according to the invention, the loop 8 may take several configurations as a function of needs. For example, in the variant embodiment shown partially in FIG. 1 a, the sections 2 a of the web 2 located upstream and downstream of the guide roll 9 are no longer parallel and their respective inclinations with respect to the vertical are different. It will be understood that, in such a configuration, the laws of displacement X_(t) and of speed V_(t) of the guide roll 9 will, of course, be different from those of the form of embodiment according to FIG. 1.

In another form of embodiment of the present invention, which is shown in FIG. 3, the regulating loop 8 is located above the web 2 and the guide roll 9 is located in the upper part of the latter. Under these conditions, it will be understood that the take-off roll 13 will be located above the web so as to effect a correct return thereof, and, moreover, means for tensioning this web have been provided, which are constituted by a tensioning system 11 formed by a roll 16 mounted to rotate at the end of an articulated connecting rod 17 about an axis O and which is in abutment on the web 2. This system 11 is able to perform several functions. Firstly, it makes it possible to maintain a virtually constant tension of the loop 8 despite the accelerations imposed on the web 2 during the operations. Secondly, it makes it possible to absorb the small shifts in length which may affect the loop 8 during successive cut-out cycles. Finally, it makes it possible to detect in simple manner, particularly by measuring the inclination taken by the connecting rod 17, the moment when the accumulated drifts of these shifts attain a critical threshold. Once this detection is effected, servo-control means may then intervene, particularly at the level of the feed roll 5, in order to ensure a compensation in length of the loop 8 having the effect of returning the connecting rod 17 of the tensioning system 11 to its normal operational position.

Of course, such a regulation can be ensured by mechanisms other than such systems and in particular by strain gauges which might be disposed on the shafts of a guide roll.

In order to facilitate correct synchronism of the web 2 with the cut-out roll 3 and its counterpart roll 3′, a cyclic mark may be made on the web 2, which will be synchronized with a determined angular position of the cut-out plates. In this way, at each of the cycles of rotation of the cut-out rolls 3, a comparison between the position of this mark and the position of the cut-out plates 3 b will be made. If an error in positioning is detected, it will provoke, via servo-control means, a reaction of the take-off roll 13 which will effect a correction of repositioning of the web 2.

The machine according to the invention may also be carried out in configurations in which the speed of feed V_(e) of the web 2 and/or the speed of rotation V_(c) of the shaping rolls are not constant.

It is thus ascertained in FIG. 4 a that, during the first phase, or cut-out phase, the peripheral speed V_(c) of the cut-out rolls 3 and the speed of feed V_(n) of the web 2 at these cut-out rolls which is ensured by the take-off roll 13, are equal, which is, of course, necessary for a correct cut-out operation. It is also ascertained in this Figure that the speed of feed V_(e) is different and constant, and thus remains so not only during the cut-out phase but also during the end-of-cycle phase.

During the latter, which begins when the cut-out rolls 3 are in the position shown in FIG. 2 a, it is ascertained that the speed V_(n) of the web 2 decreases regularly, reverses, remains constant during a short fraction of time, then re-accelerates in the normal direction, to attain a speed V_(n)=V_(c) when the following cut-out phase will begin, as shown in FIG. 2 b.

FIG. 4 b shows, during the two phases previously taken into account, namely the cut-out phase and the end-of-cycle phase, the linear positioning of the different elements. It is thus ascertained that, during the first phase, or cut-out phase, the linear positioning of the web and that of the periphery of the cut-out plate, are identical, which is of course necessary for the quality of the cut-out. It is then ascertained that, during the second phase, or end-of-cycle phase, the inclination of the straight line (speed) expressing X_(c), i.e. the positioning of the points of the plate, remains constant and that, inversely, the curve expressing X_(n) varies, the inclination of this curve decreasing in order then to increase, and it is also ascertained that, at the end of end-of-cycle phase, the advance of the web at the entry is equal to the advance of the web at the exit, this being expressed by point A in FIG. 4 b. It is also ascertained that, at that point A, the tangent zz′ to the curve X_(n) is parallel to the curve X_(c), which shows that, at the start of a new cycle, the speed of the web which enters in the cut-out rolls 3 is equal to the peripheral speed of the latter.

The apparatus according to the invention also makes it possible to effect shaping of webs in which the entry speed V_(e) is variable in accordance with a well-determined specific law of variation which is a function of the type of work effected. FIG. 5 thus shows the operational parameters of the apparatus, concerning the positioning X_(c) of the cut-out plates, of the web upstream of the cut-out rolls X_(n) (curve in broken lines), of the web at the level of its feed X_(e) and from which the positioning of the guide roll 9 X_(t) has been deduced.

The present form of embodiment makes it possible to place in the same machine, and successively, two shaping apparatus of the same period presenting a phase shift therebetween. FIG. 6 thus shows an apparatus P₁ of which it is seen that the cut-out plates are located at the beginning of cut-out phase, and a second apparatus P₂ located upstream of the apparatus P₁ and of which it is seen that the cut-out rolls present a phase shift a with respect to the cut-out roll of the apparatus P₁. Thanks to the regulating module 7, the present invention makes it possible to compensate the phase shift of these two apparatus of the same period.

The present invention also enables machines to be made, comprising apparatus of different periods and, in addition, presenting a phase shift.

The present invention also makes it possible to compensate variations in the peripheral speed V_(c) of the shaping rolls in the course of the same shaping cycle, which variations make it possible for example to minimize the accelerations of the web (by the reduction of V_(c)), by giving the latter more time to effect its to and fro movement. In the event of the plate 3 b being of short length, it also makes it possible to increase this time the peripheral speed V_(c) during the end-of-cycle phase, this making it possible to reduce the duration of the total cycle.

The present invention may, of course, be used with shaping means other than cut-out means and might advantageously be applied to fold-marking means, embossing means, stamping means, etc. . . .

The displacement of the guide element 9 may be other than linear, and in particular be circular. As schematically shown in the form of embodiment of FIG. 7, the guide roll 9 is mounted on a support sub-assembly 20, particularly constituted by two plates 21 connected in their upper part by a beam 23, this support being mounted to move in rotation about a shaft 22. This shaft 22 also constitutes the support of a regulating roll 24 which is tangential to the guide roll 9. The web 2 is brought by the feed roll 5, abuts on the regulating roll 24 in order then to be admitted between the latter and the guide roll 9 around which it winds in order finally to go towards the take-off roll 13, between which and its counterpart roll 13′ it is admitted. It will be understood that, when the support 20 pivots about the shaft 22, so that the shaft 25 of the guide roll 9 follows the broken line C, the length of the loop 8 increases or decreases depending on the direction of this rotation. In order to minimize the friction between the web and the rolls 9 and 24, these two rolls may be provided with means such as gears ensuring their connection in rotation. The law of displacement and of speed of the guide roll 9 will then be determined in accordance with the arc of circle C.

The arrangement shown in FIG. 7 may be simplified mechanically by attributing several functions to certain of the rolls. FIG. 10 shows such an example of embodiment in which the regulating roll 24 has been replaced by the take-off roll 13. The counterpart roll 13′ thereof is disposed above the latter. In this configuration, it is understood that the roll 13 performs two functions here, namely its function of take-off, as defined in the preceding forms of embodiment, and the function performed previously by the regulating roll 24. As in the form of embodiment shown in FIG. 7, the regulating/take-off roll 13 and the guide roll 9 are disposed on a support 20 adapted to pivot about the shaft 22 merged with the axis of rotation of the regulating/take-off roll 13. As previously, when the support 20 pivots about shaft 22, so that the shaft 25 of the guide roll 9 follows the broken line C, the length of the loop 8 increases or decreases depending on the direction of this rotation.

In the variant embodiment shown in FIG. 8, it is arranged that the sub-assembly 20, besides its function of controlling accumulation of the web 2, performs, in addition, a second function, namely that performed previously by the take-off roll 13 and its counterpart roll 13′, namely to ensure control of the web upstream of the shaping roll 3. Such control will thus be obtained by a more or less great oscillation.

According to the invention, it might also be possible to use the guide roll 9 as take-off roll instead and in place of the rolls 13 and 13′. In such a modus operandi, it is the guide roll 9 which performs the function of control of positioning X_(n) and of speed V_(n) of the web 2 previously performed by the rolls 13 and 13′. In this modus operandi, the rolls 13 and 13′ are in that case animated by a speed of rotation giving them an overspeed with respect to the web 2, with the result that they permanently slip thereon. 

1. Apparatus for shaping a web (2) made of a flexible material, comprising at least one feed roll (5, 5′) adapted to deliver the web (2) continuously in accordance with a law of given displacement (X_(e)) and speed (V_(e)), a shaping roll (3) associated with a counterpart roll (3′) adapted to shape the web over at least a part of its peripheral length, this shaping roll being constituted by a support roll (3 a) on which at least one interchangeable shaping element (3 b) is added, fixed on its outer surface, and which is animated by a movement of rotation in accordance with a law of given displacement (X_(c)) and speed (V_(c)), characterized in that it comprises, between the feed roll (5) and the shaping roll (3), a regulating module (7) provided with take-off means (13, 13′; 9, 9′) adapted to control the displacement (X_(n)) and the speed (V_(n)) of the web (1) upstream of the shaping roll (3) and at least one mobile guide element (9, 9′) adapted to exert on at least one buffer loop (8) of the web (2) formed between said rolls (5, 3), a positive guiding of which the displacement is controlled in accordance with a determined law.
 2. Apparatus according to claim 1, characterized in that the law of displacement of the mobile guide element (9, 9′) of the web (2) is a function of the law of displacement (X_(e)) of the feed roll (5, 5′) and of the law of displacement (X_(n)) of the take-off means (13, 13′), itself a function of the law of displacement (X_(c)) of the shaping roll (3).
 3. Apparatus according to claim 1, characterized in that the take-off means are constituted by at least one roll (13, 13′).
 4. Apparatus according to claim 1, characterized in that the take-off means are constituted by the mobile guide element (9), the latter being formed by a rotating roll around which the web (2) winds; at least one rotating roll (13, 13′) animated by a peripheral speed greater than that of the web (2) being disposed between the shaping roll (3) and the guide roll (9).
 5. Apparatus according to claim 2, characterized in that the guide element (9) is constituted by a rotating roll around which the web (2) winds.
 6. Apparatus according to claim 2, characterized in that the guide element (9) is constituted by a piece (9′) fixed in rotation, around which the web (2) winds.
 7. Apparatus according to claim 6, characterized in that the guide element (9′) is provided with means for blowing a gas adapted to create between itself and the web (2) a cushion of gas.
 8. Apparatus according to claim 1, characterized in that the displacement of the guide element (9, 9′) is linear.
 9. Apparatus according to claim 8, characterized in that the linear displacement of the guide element (9, 9′) is obtained by a linear motor comprising primary and secondary poles mobile with respect to each other and means for controlling their relative movements, the guide element (9, 9′) being fast with one of these poles.
 10. Apparatus according to claim 8, characterized in that the linear displacement of the guide element is obtained by a system constituted by a connecting rod (10) articulated at one of its ends on the latter and at its other end on a crank (12) whose angular position determines the linear function of the guide element (9′).
 11. Apparatus according to claim 1, characterized in that the displacement of the guide element (9, 9′) is circular.
 12. Apparatus according to claim 11, characterized in that the guide element is constituted by a guide roll (9) arranged so that it is adapted, in the course of its displacement, to remain tangential to another roll (24, 13), the web (2) being admitted between these rolls (9, 24, 13) and winding around the latter in order then to go in the direction of the shaping roll (3).
 13. Apparatus according to claim 12, characterized in that said other roll is constituted by a regulating roll (24).
 14. Apparatus according to claim 12, characterized in that said other roll is constituted by the take-off roll (13).
 15. Apparatus according to claim 13, characterized in that the circular displacement of the guide (9) and regulating (24) rolls ensures control of position (X_(n)) and of speed (V_(n)) of the web upstream of the shaping roll (3).
 16. Apparatus according to claim 12, characterized in that the guide roll (9) and said other roll are servo-controlled by each other in rotation.
 17. Apparatus according to claim 1, characterized in that it comprises, between the feed roll (5) and the take-off means (13), a system (11) for controlling the tension of the web.
 18. Apparatus according to claim 17, characterized in that the feed roll (5) is servo-controlled by the system for controlling the tension of the web so as to ensure maintenance of the tension of the latter at a constant value.
 19. Apparatus according to claim 1, characterized in that it comprises means adapted to read a cyclic mark disposed on the web, to compare the position thereof with a reference of position of the shaping roll and, as a function of this comparison, to modify the positioning of the web with respect to the shaping roll. 